Hydraulic rotary barrel pumps or motors



United States Patent Inventor Rene Lucien Neuilly sur Seine, France Appl. No. 598,410

Filed Dec. 1, 1966 Patented Dec. 8, 1970 Assignee Societe Anonyme dite: Messier Paris, France Priority Dec. 3, 1965 France No. 40,932

HYDRAULIC ROTARY BARREL PUMPS O MOTORS 5 Claims, 4 Drawing Figs.

0.8. CI. 91/507 Int. Cl. F04b l/02 Field of Search 103/162,

I62(A). 162(V): 230/178; 92/57: 91/198: 123/43(A),43(A.1)

References Cited UNITED STATES PATENTS Primary Examiner-William L. Freeh Att0rney-Waters, Roditi, Schwartz & Nissen ABSTRACT: A hydraulic pump or motor of the so-called rotating and floating barrel type wherein a bearing is placed between a fixed support and the barrel, the bearing being of small diameter and disposed at the point of application on the geometric axis of the barrel of the resultant of the shearing forces applied to the barrel so as to absorb said shearing forces and permit the barrel to make slight angular movements with 1,886,492 ll/1932 Mattson 123/43 respectto the geometric axis.

3 .5 T ix 9v I r r" 8 a 3,545,338 HYDRAULIC ROTARY BARREL PUMPSOR MOTORS Barrel pumps of a known type comprise a cylindrical frame The present invention relates to hydraulic; rotary barrel 1 closed at its extremity by a bottom 2., in which are formed pumps or motors with distribution valve-gear of the so-called fluid admission and delivery orifices (not shown). A barrel 3 slide-face type. In the description which follows below. driven by a shaft 4 moves in the interior of the frame, 1,

reference wi be m d 9 t p mp O this typ it i remaining closely applied at one of its extremities against the understood that the arrangements described are equally ,apflat internal face of the bottom 2-the slide-face-in order to plicable to hydraulic motors. and that this application falls a ut lter t l in ni tio d i h course f i within the scope of the invention. rotation, cylinders formed in the barrel (not shown), which t P p of this kind, t suction of the fluid into the y opeh out into the saidextremity and inside which pistons Sare tiers of the barrel and its delivery under pressure from the said 10 d t d to move, Th reciprocating motion f th pistons i cylinders is effect d th ugh t Ports in a Plate slide-face effected in known manner by a plate 6 inclined to the axis of perpendicular t the axis ofthe g inst which isapplied the barrel, against which shoes 7, coupled to the universal a corresponding plane surface of the said barrel. The cylinders h d j im s of h pistons are i bbi b a P this Plane sutface hhd communicate shceesstvely i The force E due to the pressurewithstood by thepistons can proposedto mount the barrel on a bearing arranged at the ex- With one e other of the said Potts th the Shdtt'tace during be resolved into a force F perpendicular to the plate 6 and a course h 9 e batteti shearing force T perpendicular to the axis of the pump. The

It I ft know" h these p p must C P Y resultant of these shearing forces, 2T ishalso perpendicular to w e h t cohdttlohs: the axis, its point of application being the point of intersection The sheal'thg forces due to the Pressure to whtch the of this axis with the plane defined by the centers of the univerrel is subjected must be compensated in the most ad- Sa| joints 8 vantageous manner, and the most logical solution consists In accordance with the invention, a bearing f small diame- 0f teststthg the resultant of these forces at the Point of its r ter is provided inside the barrel 3, between the barrel and the apphcattoh Oh the ofthe h- 1 support 9, coaxial with the shaft 4 which passes through it, in The barrel must be mounted h that h It must order to absorb the resultant of the shearing forces at the point be able to make small angular displacements with respect ofits application to the of the Pump m order to he cohstahhyt and This bearing can beconstituted by a roller bearing 10 (FIG.

fectty applied agaihst the h h' 2) for example a needle bearing, or it may be in the form of a In order to comply with these conditions, it has already been jbuma] bearing, this latter Solution havingcettain advantages terior of the barrel level with the resultant of the shearing 3 fol, some types ofpumps especlany pumps ofsmau output and of very. small size; The bearing may also be in the form of a {2221;3 5:212523232 3352 belhg f' by fluid bearing Ol'lt may be a bearing of any other type.

However, this solution implies the use of a bearing witha large diameter, which involves many disadvantages. In particular, the power absorbed by the bearing is considerable, which reduces the efficiency in the case of applications at high speeds of rotation, and thepiston controlling the inclination of the plate, which regulates the output of the pump in known manner, must be mounted far from the axis of the pump, which resultsin an increase in the external diameter in the case of self-regulatingpumps. 1

to permit the barrel to make slight angular movements with respect to its axis, in order that it may remain constantly applied in a perfect manneragainst the slide-face of the pump.

The freedom of movement of the barrel is further ensured -by a driving system which forms part of the invention, and

which is illustrated in FIG. 2. It comprises a driving sleeve 11, 40 t of which one long portion 11a is directly actuated by the shaft ;4 with which it cooperates, for example. through the inter- The internal seating 9a of the bearing is slightly domed so aslmediary of a system of splines','and of "which one shorter por- Thepresent invention has fonts ob ect to prov de a hydraumm coupled to that, p i g y a F web p he barrel pump which is mounted floating and which does not present the disadvantages outlined above, and in which abeard'rectly drives the bane] example by means System ing of small diameter is arranged in the interior of the pump lofsphhesbarrel so as to resist the shearing forces due to the pressure, at h method dnvmg emplfyed lhcomblhahoh the a the point of application of their resultant, and to give the bargbeanhg f takmg up the shearmg forces defined above has rel the small amount of freedom of movement which is neceshumerohs advantages" In fact by reasohhof the short lehgth of Sam ;the portion 11b, the barrel can readily move away to a As the bearing is of small size, the power absorbed by it is idtstahce c from am of the P the beahhg 10 very small, and as it is mounted inside the barrel, the pump h ahgthahy displaced over the domed Surface f- If a may have a small external diameter, even in the case of a selfi f h the h' between h Sleeve and theheatthg regulating Pump, since the piston operating the regulating iwhile IS the distance between this bearing and the bearing 12 plate may in this case be arranged close to the axis of the t whlchthe Support 915 h i It clear that h barrel pump and the plate may also have a f jcan readily move angularly with respect to the 3XIS of the In order to permit slight angular displacements, it ,is only P p through an angle odefihed y tan (J necessary to give the bearing a slightly domed internal seating m and to provide a driving system which will permit such move ments, for example to use a driving sleeve comprising. a rela- The lengths of the sPhhes ofthe P9 and 11b of the tivcly long portion fixed to one of the extremities f th M sleeve 11 are naturally a function of the diameters of the shaft ing shaft and coupled by a radial web to a short portion which 4, the Pottloh and the Portloh directly dri he ba r l, The driving system described above may however be The invention will be described in detail with reference to replaced by y other desired method of driving which P the accompanying drawing. mits a slight angular displacement of thebarrel, such as for ex- In the drawing: ample a cardan joint or the like. FIG. I is a diagrammatic view in partial axial section of a As already stated, the fact of utilizing a bearinglO mounted pump comprising thearrangements in accordance withihe i inside the barrel makes it possible to employ a bearing having vention; dimensions considerably smaller than those of an external FIG. 2 is a detail section on a larger scale, illustrating the bearing, sin the tangential speeds e Q the other 1 driving system of the barrel of this pump and the floating hand, the small dimensions of the internal bearing obviously mounting of this barrel; ensure a better efficiency of the pump.

FIG. 3 is an axial cross section of a constant output pump in The invention having been described in respect of its princiaccordance with the invention; and ple, it will now be described by way of example and without FIG. 4 is an axial half-section of an alternative form of the limitation, in its application to a constant output pump illuspump according to the invention. L trated in FIG. 3, and to FIG. 4 showing an alternative form ap- Referring first to FIGS. I and 2i i plicable to any type of pump in accordance with the invention.

The constant output pump illustrated in FIG. 3 differs very little from that which is shown in FIG. 1. The parts already referred to have been given the same reference numbers and will not be described in detail.

In FIG. 3, the cylinders 14 provided in the barrel 3 have been shown. The barrel is applied in known manner against the slide-face 2 by a spring 16 which is interposed between a ring 17 fixed on the shaft 4 and the web 11c of the sleeve 11. The operation of a pump of this type is well known and will not therefore be described.

It will be noted that the pump shown in FIG. 3 comprises a barrel made of one piece and therefore of one material only.

The different parts of the barrel are not however subjected to the same stresses and there is no material which can be utilized indifferently for all these parts. It is in fact preferable that the extremity of the barrelapplied against the slide-face should be of a material having a low hardness, whereas the seating of the bearing and also, where applicable, the part subjected to the driving torque of the sleeve 11, must be as hard as possible.

The arrangements of the bearing 10 and the sleeve 11 particular to the invention make it possible to utilize a composite barrel 3 consisting of only two parts of materials of different kinds, depending on the purposes desired. Thus, for example, FIG. 4 shows an alternative form of the pump, in which the barrel 3 is composed of two parts, one 311 being supported against the slide-face 2 and of a relatively soft material, while the other 3b, cooperates with the sleeve 11 and the bearing 10, and is of a relatively hard material.

It should be noted that a barrel of this kind is simple since, with a bearing mounted outside the barrel for taking up the shearing forces, it would be very difficult, if not impossible, to utilize a composite barrel comprising only two parts of different kinds. In the case of use ofa journal bearing, a layer of antifriction material can of course be applied on the internal face of the portion 3b.

In all the pumps which have been described above, the pistons are parallel to the axis of the barrel. They could of course be equally well inclined to that axis.

In the same way, the hollow support which serves as aninternal seating for the bearing which absorbs the shearing forces could equally well be a solid support, the outlet of the driving shaft being then effected through the bottom of the The bearing which absorbs the shearing forces may equally well be supported on a ring fittedover the support.

The support may also be anchored to the bottom, the outlet of the driving shaft then being effected either through the bottom or through the opposite extremity.

As has already been indicated, all the characteristics of the pumps which have just been described could also be applied to rotating barrel hydraulic motors, without thereby departing from the scope of the invention.

I claim:

1. A hydraulic pump or motor of the so-called rotating and floating barrel type, comprising a cylindrical fixed casing provided with a bottom having a slide-face with first and second orifices therein; a barrel supported in said casing for rotation about an axis, said barrel having cylinders and slidable pistons in said cylinders; means for placing said cylinders into communication alternately with said first and second orifices in said slide-face; means for reciprocally moving said pistons in said cylinders and producing forces on said pistons having components acting as shear forces applied to said barrel; a shaft mounted for rotation with respect to said casing about an axis substantially coincident with the axis of rotation of said barrel; a sleeve concentric with said shaft, said sleeve being traversed by said shaft and disposed in the interior of said barrel; means for coupling a relatively long portion of a said sleeve to said shaft and means for coupling a relatively short portion of said sleeve to said barrel; a support rigidly fixed to said casing, said support being coaxial with said shaft and interposed between said shaft and said barrel; and a bearing interposed between said support and said barrel, said bearing being disposed at the point of application on the axis of said barrel of the resultant of the shearing forces applied to said barrel, said support including a slightly domed portion constituting a seating for said bearing.

2. A hydraulic pump or motor as claimed in claim 1 wherein said means coupling said relatively long portion of said sleeve to said shaft comprises a system of splines between said sleeve and shaft, and said means coupling said short portion of said sleeve with said barrel comprises a second system of splines between said sleeve and barrel.

3. A hydraulic pump or motor as claimed in claim 1 wherein said barrel is a composite barrel comprising two parts rigidly fixed to each other, one of said parts being constituted by a relatively soft material and being supported against said slideface, while the other part is constituted by a relatively hard material and cooperates with said sleeve and said bearing.

4. A hydraulic pump or motor as claimed in claim 2 wherein said barrel is a composite barrel comprising two parts rigidly fixed to each other, one of said parts being constituted by a relatively soft material and being supported against said slideface, while the other part is constituted by a relatively hard material and cooperates with said sleeve and said bearing.

5. A hydraulic pump or motor as claimed in claim 1 in which said shaft passes through said support. 

